High-pressure plunger compressor

ABSTRACT

The present invention relates to devices designed for building up high pressures. A high-pressure plunger compressor comprises a cylinder with a compression chamber. Pressed to the cylinder is a piston with a discharge channel. A plunger is passed with a clearance through the compression chamber. The cylinder with the compression chamber is arranged in a clamp coaxially with respect to a clearance forming an annular space. The annular space is sealed on the side facing the piston end and on the side of the base of a conical portion of a sealing bushing. In addition, the annular space on its end communicates with the channel intended for the discharge of compressed working fluid. A gas or liquid can be used as the compressed working fluid. This invention makes possible an extended service life of the cylinder with the compression chamber.

United States Patent Vereschagin et al.

[451 Dec. 11,1973

2,612,841 10/1952 Lasley ..4l7/50l 2,204,626 6/1940 Scott 417/437 3,490,344 l/l970 Archer et 31.... ..92/169 3,119,410 1/1964 Noecker ..4l7/569 Primary Examiner-William L. F'reeh Assistant Examiner-Gregory LaPointe Attorney-Holman & Stern [57] ABSTRACT The present invention relates to devices designed for building up high pressures. A high-pressure plunger compressor comprises a cylinder with a compression chamber. Pressed to the cylinder is a piston with a discharge channel. A plunger is passed with a clearance through the compression chamber. The cylinder with the compression chamber is arranged in a clamp coaxially with respect to a clearance forming an annular space. The annular space is sealed on the side facing the piston end and on the side of the base of a conical portion of a sealing bushing. In addition, the annular space on its end communicates with the channel intended for the discharge of compressed working fluid. A gas or liquid can be used as the compressed working fluid. This invention makes possible an extended service life' of the cylinder with the compression chamber.

3 Claims, 5 Drawing Figures 1 1 HIGH-PRESSURE PLUNGER COMPRESSOR [76] Inventors: Leonid Fedorovich Vereschagin,

Kutuzovsky prospekt, 2/1, kv. 231; Jury Sergeevieh Konyaev, ulitsa Fersmana, 11, kv. 26; Evgeny Valentinovich Polyakov, Belyaeyo-Bogorodskoe, 39, kv. 73, all of Moscow; Ivan Eiimovich Surkov, ulitsa Shkolnaya, 6, kv. 53, Moskovskaya Oblast, all of U.S.S.R.

[22] Filed: July 14, 1971 [21] Appl. No.: 162,424

[30] Foreign Application Priority Data July 23, 1970 U.S.S.R 1453652 [52] US. Cl. 417/501, 92/171 [51] Int. Cl. F04b 7/04 [58] Field of Search 417/499, 501, 569, 417/570, 571;92/169,171,165,166,167, 168; 137/4544, 454.6

[56] References Cited UNITED STATES PATENTS 3,128,941 4/1964 Waibel 92/257 3,446,427 5/1969 Vereschagin et al. 417/501 I HIGH-PRESSURE PLUNGER COMPRESSOR BACKGROUND OF THE INVENTION The present invention relates to devices designed for building up high pressures in a liquid or gas and, more particularly, it relates to high-pressure plunger compressors. I

PRIOR ART There are known high-pressure plunger compressors comprising a piston and a cylinder with a compression chamber, the piston beingpressed against the cylinder. Through said chamber a plunger passes with a clearance. The latter clearance serves to accommodate a sealing bushing which features on the side of the compression chamber of the compressor a hollow truncated cone and is provided in its other portion with inlet channels for the supply of compressed working fluid to the compression chamber. The piston is provided with a discharge channel for the delivery of the compressed fluid to the user.

At sufficiently high pressures of the compressed working fluid, compression stresses in the cylinder turn to tensile stresses, which cause alternating loads upon the cylinder.

In the above-mentioned known compression the cylinder features a low fatigue strength due to the effect of alternating loads acting thereupon.

In order to increase the fatigue strength of the cylinder, in the latterthere are created initial compression stresses either by tight-fitting the cylinder in a set of concentric rings which, in turn, are tight-fitted one in the other, or by self-loading the cylinder, i.e.,;providing inside the cylinder pressures which exceed the working pressure and cause plastic deformation.

Said pre-generated compression stresses decrease upon the effect of the compressed working fluid on the inner surface of the cylinder.

However, the afore-described technique employed during the plunger compressoroperation under pressures on thefiorder of 16 kilobars does not provide for the elimination of tensile stresses to avoid alternating loads.

OBJECTS AND SUMMARY OF THE INVENTION The present invention has for its object an increase of the service life of a cylinder operating under compressed working fluid pressure on the order of 16 to 20 kilobars.

Another object of the invention is to improve the reliability of the compressor operation.

For accomplishingthese and other objects,

the cylinder with the compression chamber is arranged in a clamp coaxially with respect to a clearance forming an annular space which is sealed on the side .the cylinder experiences only compression stresses throughout the who'le'working cycle of the compressor.

It is preferable that the annular space communicate with the compressed working fluid discharge channel through the channels provided either in the piston end or in the cylinder end.

The supply of the compressed working fluid to the annular space from the end through thechannels provided in the piston end or in the cylinder end helps increase the service life of the clamp, due to the absence of laterally extending bores in the latter, which bores should have otherwise served as concentrators of stresses. This, in turn, brings about an increased reliability of the compressor as a whole at working pressures on the order of from 16 to 20 kilobars.

The plunger compressor, according to the present invention, featuring overall dimensions together with the drive of 2,000 X 900 X 1,700 mm provides for the compression of liquids to a pressure of 20 kilobars at an efficiency of 16 litres of compressed liquid per hour and for the compression of gases to a pressure of 18 kilobars at an efficiencyof 8.9 X 10? cum/hr. and suction pressure of 800 bars.

BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a view in vertical section, with certain components in elevation of a compressor embodying the invention. l

FIG. 2 is a fragmentary view in vertical section with the plunger. and delivery valve in elevation showing the manner of supplying compressed working fluid to the working space,

FIG. 3 is a view taken along the line 3-3 of FIG. 2, FIG. 4 is a view similar to FIG. 2 illustrating another mannertof supplying compressed working fluid to the working space, and r 1 FIG. 5 is a view taken along the line 5--5 of FIG. 4.

Detailed Description of the Invention Referring now to FIG. 1 of the drawings, the plunger compressor according to the present invention comprises a split head 1 formed by a socket 2 with a housing 3, and a crank gear 4. The socket 2 is connected to the crank gear 4 by means of a bracket 5. The socket 2 accommodates a piston 6 provided with a delivery valve 7, and a clamp 8. The piston 6 is also provided with discharge channels'9, l0 and 11. In the clamp 8, defined, for example, as concentric rings tightly-fitted to each other, there is arranged a cylinder 12 having a compression chamber. The cylinder 12 is arranged coaxially with a clearance which forms an annular space 13. The cylinder 12 is centered with respect to the clamp 8 by means of a ring 14. A plunger 15 passes, with a clearance, through the compression chamber of the cylinder 12. This clearance is meant for the accommodation therein of a sealing bushing 16 which has a conical portion 17 (see FIG. 2) on the side of the compression chamber and a base 18 in which provision is made for inlet channels 19 for the delivery, to the compression chamber, of compressed working fluid consisting of liquid or gas.

The annular space 13 is hermetically sealed on the side of the end of the piston 6 as a result of a sealing collar 20 (FIG. 2) being pressed against the clamp 8, and on the side of the base 18 of the conical portion 17 of the sealing bushing 16 as a result of the clamp 8 and the cylinder 12 being pressed bythe piston 6 against the base 18 of the sealing bushing 16, due to the pressure delivery to the piston 6. The delivery of pressure, for example, oil pressure, is effected by two pressure generators, namely, a pump 21 through non-return valve 22 and a'melting pump 23 having a doublediameter piston 24. The smaller and larger ends of the piston 24 are acted upon, respectively, by the compressor delivery pressures and by the sealing pressure supplied to the piston 6.

The annular space 13 communicates with the compressed working fluid discharge channel 9 through annular channel 25 and radial channels 26, as shown in FIG. 3, which channels are provided in the piston end and serve for the supply of the compressed working fluid to the space 13 from the end from the channel 9 positioned directly after the delivery valve 7. The radial channels 26 communicate with the annular channel 23, which is arranged opposite the annular space 13.

The high-pressure plunger compressor according to the present invention operates in the following manner:

The compressed working fluid is supplied through a a channel provided in the housing 3 to the inlet channels 19 of the sealing bushing 16 and, at the moment the plunger 15 is in the lowermost position, fills the working volume of the compression chamber. While moving upwards, the plunger 15 having reached the base 18 of the conical-portion 17 of the sealing bushing 16 closes the inlet channels 19 thereof and effects the compression-of the working fluid. After the pressure of the compressed working fluid has exceeded the pressure behind the delivery valve 7, the valve 7 opens to allow the compressed working fluid pass through the channels 9, 10 and 11 of the piston 6 to the user.

Concurrently, the compressed working fluid is supplied-through the circular channel 25 and the radial channels 26.to the annular space 13 and develops a compression stress in the material of the cylinder 12, thereby relieving the latter of alternating loads. By relieving the cylinder 12 of alternating loads, its service life is increased. The supply of the compressed working fluid to the annular space from the 'end helps increase the life of the clamp 8, due to the absence in the latter of laterally extending bores which could have served as concentrators of stresses.

When supplying the compressed working fluid to the working space in a different way, as shown in FIG. 4, the annular space 13 communicates with the compressed working fluid discharge channel 9 with the aid of radially extending channels 27 provided in the end of the cylinder 12. At the same time the compressor as a whole operates in a manner similar to that described hereinabove, except that the working fluid being compressed passes to the annular space 13 through the radially extending channels 27.

What we claim is:

l. A high pressure plunger compressor, comprising: a cylinder provided with a compression chamber; a piston having a discharge channel and a sealing collar, said piston being pressed by said sealing collar against said cylinder; a plunger passing with a clearance through said compression chamber; a hollow sealing bushing accomodated in said clearance one portion of said bushing having the shape of a truncated cone on the side of said compression chamber and the remaining portion of said bushing having inlet channels for the supply of working fluid being compressed to said compression chamber; a claim, said cylinder with the-compression chamber being arranged coaxially within the clamp to provide an annular space between the cylinder and clamp; said annular space being hermetically sealed on the side facing the end of the piston as a result of said sealing collar of said piston being pressed against said clamp, and on the side of the base of the conical portion of said sealing bushing as a result of the clamp and the cylinder being pressed by said piston against the base of said sealing bushing and communicating on the side of the end facing said piston with said channel adapted for the discharge of the compressed working fluid.

2. The high-pressure plunger compressor as claimed in claim 1, wherein said annular space communicates on the side of its end facing said piston with said channel adapted for the discharge of the compressed working fluid by means of radial channels provided in the end of said piston, and an annular channel arranged opposite said annular space, with the radial channels communicating with the annular channel.

3. The high-pressure plunger compressor as claimed in claim 1, wherein said annular space communicates on the side of its end facing said piston with said channel adapted for the discharge of the compressed working fluid by means of radial channels provided in the end of said cylinder. 

1. A high pressure plunger compressor, comprising: a cylinder provided with a compression chamber; a piston having a discharge channel and a sealing collar, said piston being pressed by said sealing collar against said cylinder; a plunger passing with a clearance through said compression chamber; a hollow sealing bushing accomodated in said clearance one portion of said bushing having the shape of a truncated cone on the side of said compression chamber and the remaining portion of said bushing having inlet channels for the supply of working fluid being compressed to said compression chamber; a claim, said cylinder with the compression chamber being arranged coaxially within the clamp to provide an annular space between the cylinder and clamp; said annular space being hermetically sealed on the side facing the end of the piston as a result of said sealing collar of said piston being pressed against said clamp, and on the side of the base of the conical portion of said sealing bushing as a result of the clamp and the cylinder being pressed by said piston against the base Of said sealing bushing and communicating on the side of the end facing said piston with said channel adapted for the discharge of the compressed working fluid.
 2. The high-pressure plunger compressor as claimed in claim 1, wherein said annular space communicates on the side of its end facing said piston with said channel adapted for the discharge of the compressed working fluid by means of radial channels provided in the end of said piston, and an annular channel arranged opposite said annular space, with the radial channels communicating with the annular channel.
 3. The high-pressure plunger compressor as claimed in claim 1, wherein said annular space communicates on the side of its end facing said piston with said channel adapted for the discharge of the compressed working fluid by means of radial channels provided in the end of said cylinder. 